Web roll controlling mechanism



April 18,1944 c. s. CAFFREY WEB ROLL CONTROLLING MECHANISM l Filed May 17, 1940 5 Sheets-Sheet l :g1-wwwa@ @fl/M255 cnn-RE);

April 1s, 1944. CAFFREY 2,346,903

WEB ROLL CONTROLLING MECHANISM Filed May 1'7, 1940 5 Sheets-Sheet 2 l $2, RJ'MLMY @Mw .April 18, 1944- c. s. CAFFREY I g 2,345,903

AWEB ROLL CONTROLLING MECHANISM Filed May 1'7, 1940 5 Sheets-Sheet 5` April 18, 1944. c. s. CAFFREY WEB ROLL CONTROLLING MECHANISM 5 Sheets-Sheet 4 Filed May 17, 1940 g 3mm April 18, 1944 c. s. CAFFREY 2,346,903

` I WEB ROLL CONTROLLING MECHANISM 5 ShPA-cs-Shee'fI 5 Filed May 17, 1940 g @43 Q ',LMY

worum.;

Patented pr. 18, 1944 WEB ROLL coNTRoLLING MECHANISM Charles S. Carey, Port Washington, N. Y., assignor to Wood Newspaper Machineryorporation, Plainfield,

Virginia a corporation o! Application May 17, 1940, SerialNo. 335,855

12 Claims.

This invention relates to web roll controlling mechanisms.

In certain kinds of web treatment, and particularly in processsing paper stock, it is necessary to maintain a relativelyheavyI tensionv on both the unwinding and winding ends of the travelling paper web while portions of the web intermediate these ends are being operated upon at work stations, such as in calender machines. This tension is particularly great at the unwinding end of the web where the tension may be as much as the web will withstand without rupture. Under such conditions there is a great loss of power under present practice, and it is a difficult problem to maintain a constant tensionv on both ends of the web at the same timewhen the intermediate portion is being subjected to a calendering operation.

One of the objects of the present invention is to produce a better finished roll by automatically maintaining a constant winding tension through` out the roll as it increases in diameter.

Another object of the present invention is to unwind a roll by automatically maintaining a constant web tension throughout the unwinding period of the roll.

A further feature of the present invention provides a construction that allows the operation of the machine almost continuously by materially reducingthe time lost in removing the wound roll and replacing it with an empty roll, it being only necessary for `the machine to be stopped for a short time necessary to make the splice in the web.H

'QA still further advantage in the construction of theV present invention resides in the elimination of rollspindle shafts and using chucks instead.

Another feature of this invention is saving in power. n the unwinding yend the power customarilywasted innr'etarding Vthe unwinding roll is translated through the variable speed drive and its chain drives, ba'ck into the machine. On the winding end there is a constant slip, and therel fore power loss of percent from the beginning of the wind to the finished roll, whereas the loss,

when winding with a conventional slip belt, in-

fcreases rapidly as the rol1increases in diamete: `start-ing at 10 per cent, and terminating in aslip approaching 100 per cent where a large diame 'er roll is wound `on a small core.

' It'may befound that a uniformlywiapped roll does not prove satisfactory under certain condi-- tions such as severe changes' in temperature or humidity. A roll that is wrapped tightly at the core and more loosely toward the circumference would allow for contraction or expansion withoutA any appreciable change in the paper roll diameter. It is an additional feature of the present invention to provide mechanism whereby the degree of the tightness of the wrap may be regulated throughout the thickness of the roll.

With the foregoing and other objects in view, the invention is set forth in the accompanying specification and illustrated in the drawings for the purpose of teaching its application, but it is to be'understood the changes, variations and modications may be resorted to without departing from the scope o f the invention defined by the claims hereunto appended.

In the drawings, wherein the preferred form of the invention is illustrated:

Figure 1 is a more or less diagrammatic arrangement of the entire assembly in the nature of a side elevation showing the general arrangement of the three-arm reel, control and drive units, and the calender stack of the present invention.

Figure -2 is a fragmentary planview ythereof partly in section showing the arrangement between the drive units.

Figure 3 is a diagrammatic view of the position of a three-arm reel with one roll unwinding, one

roll winding, and a third full roll to be processed on one of the reel arms ready to replace the roll being unwound when the same is spent.

Figure 4 isa view similar to Figure 3, with the web severed from the rolls after completion of unwinding and winding.

Figure 5 is a view similar to Figure with the reel arms rotated 120 from the position shown in Figure 4, showingthe fully wound processed'roll'l preparatory to unloading, the recently unwound core in the winding position with the end of the web anchored thereto, and having the replacement roll in unwinding position having its web spliced to the web passing to the calender apparatus.

Figure 6 is a view similar to Figure 5,' showing the completed wound processed roll being removed from the reel arm in preparation to loading afull unprocessed roll on the empty ar'm while the unwinding and winding rolls are in operation.

t Figure' is an enlarged end view of one oi the transmission drive units removed from the assembly showing a fragmentary portion of the mechanism for regulating the transfer of .torque to control the web' tension.

Figure 8 is a view similar to Figure 2 illustrating a modified form of mechanism for transferring torque by the use of a belt and a tension ap- I in the unlocked position.

plying device, together with the control therefor.

Figure 9 is an elevation of one of the torque transferring mechanisms, tension applying device, the control therefor, combined with the speed changing transmission drive unit, all of which are removed from the machine.

Figure 10 is a fragmentary plan view of the reel partly broken away and removed from the assembly illustrating the manner of mounting the rolls on the reel arms.

Figure 11 is a view similar to Figure 10 illustrating a modified form of the invention for mounting the rolls on the reel arms.

Figure 12 is a fragmentary end elevation of the reel shown in Figure 11 of the drawings.

Figs. 13 and 14 are sectional views of the variable speed drive gearing contained in the two driving units.

With these foregoing objects in mind, the arrangement to be described below is designed to produce proper tension control on both unwinding and winding rolls and will save power losses. The customary means of furnishing tension on the unwinding roll is through the use of friction elements, such as friction brakes, and the like, working directly upon the roll or upon the roll shaft. It is, therefore, evident that theloss in power at this point is great. The winding end tension is controlled by slip clutches which attempt to operate the roll faster than web speed will allow.

The means to be employed to control the paper rolls in the present invention, is a variable speed drive unit connected to each roll, which is in turn regulated by a differential control unit. This type of drive may be adapted to various conditions; that is, it may be used on paper roll stands or two or three-arm reels. In the description to follow a three-arm reel installation will be discussed because of certain advantages it has over roll stands or two-arm reels.

Referring to the drawings in detail 9 indicates a reel stand in which a shaft I is journalled for selective rotation. The reel is fixed to the shaft I0 and rotates with the shaft. As illustrated in the drawings, the invention may be applied to a reel having three arms ||a spaced approximately 120 apart. In order to rotate the reel a relatively large wormwheel gear is fixed to shaft I0 outside of the stand 9.A This gear meshes with a worm gear 9| driven by an electric motor 92 mounted on stand 9 through gears 93. 94 and shaft 95. As indicated in Figure 1, reel is held in fixed position by pawl 96 which engages a notch 91, one on the end of each 'eel arm Ila. The pawl 96 rocks with a pin 98 journalled, on the stand. A handle 99 fixed to the outer end of pin 98 when operated to the right causes the release of the pawl from the engaged position in Figure 1 and frees the `reel so that it may be rotated.

To prevent any damage to the machine by premature motor operation, cam switch |00 is located in such a mapner that the electric circuit,

composed of conductors I0I, |02, |03, and switch |00, for the motor, will be interrupted-when the ,pawl operating handle 99 is in locked position,

and said circuit will be closed when the handle is It will thus be seen that the reel will be automatically rotated to working positions hereafter explained, where it is locked in fixed relation while one roll is unwinding, another is' being wound, and a third roll that has been processed is removed and replaced by a mill roll all of which will appear later.V

Rolls I2, I3 and |4 are rotatably mounted at the extremities of arms on the reel spaced from one another. A paper web I5, in thev instance illustrated, from roll I2 has an intermediate portion thereof passing through the rolls of the calender stand I6 and then is wound on roll I3. In Figure 1, the roll I4 is an unprocessed or mill roll, and has been mounted in the arm ofthe reel to replace roll I2 when the latter is completely unwound, as shown in Figure 5.

By referring to Figures 3, 4, 5 and 6, the manner of reel operation will be readily understood. Fig. 3 is similar to Fig. 1 in showing the position of the various rolls. In Fig. 4 the roll I2 seen in Fig. 3 has been unwound, leaving core |2a, and roll I3 seen in Fig. 3 becomes fully wound roll |3a. At this point the calender machine is stopped and web I5 is severed from-core |2a and roll |3a. Drive clutches to be discussed later are disconnected, and the pawls that lock the reel are released, thereby allowing the reel I I to be moved automatically through 120 as shown in Fig. 5. When the reel has been moved to the new position locking pawls, to be described, are again engaged. and in doing so, the reel is automatically stopped as will appear later. Referring to Figure 5 roll I4 has now assumed the position previously held by roll I2, and core |2a moves to the position held by roll I3. The ends of the web from the calender stack are then attached to the new roll I4 and core |2a, the variable vspeed drives are reset, and the drive clutches are connected in. The

'calender is thenI started, unwinding roll I4 and winding on the ccl |2a.

In Figure 6 the advantages of a three-arm reel will be noted. Roll |3a, which has recently been processed, is being removed from the reel by means of a loading jack I8. This may be accomplished without interfering with operations of the unwinding and winding rolls, thereby saving valuable time. With a two-arm reel it would be necessary to remove the freshly processed roll before a mill roll would be inserted.

Referring to Fig. 2, it will be noted that rolls I2 and I3 are carried in the reel arms and connected to speed changing transmission drive units 23 and 21 byclutches indicated generally at 2|, 25, respectively.

The rolls |2 v and I3, are in working position in Fig. 1 of the drawings. The spindle of roll I2 is connected by means of a clutch 2| to the output shaft 22 of the variable speed transmission drive unit 23 which in the present form is of the Reeves type. In such transmissions an edge-active belt connects adjustable V-shaped pulleys on the input and output shafts 24 and 22, respectively. similar to the Reeves transmission shown in the patent to Perry, 2,168,071, August 1, 1939. The gearing contained in units 21 and 52 is identical with the gearing contained in units 23 and 5|. This gearing is shown in Figs. 13 and 14. In Fig. 13, which shows the variable speed driving mechanisms contained in unit 21, is shown shafts 26.

- 28, 6| and Bla which correspond to the parts bearing the same numerals in Fig. 2. These shafts are mounted in suitable bearings attached to the casing of drive unit 21. Tapered cones |32 and |33 are splined to shaft 26 and cones |34 be used to slide cones |32 and |33 endwise on shaft 28 and cones |34 and |35 endwise on shaft 28 while still permitting the cones to rotate with their respective shafts. It is apparentl that when one pair of cones is Vmoved closeftogether the other pair will be moved farther apart, and vice versa. 'I'hus the tapered belt |36 will rise on one pair of cones and fall on the other, changing the effective diameters on which it operates.4 This mechanism can be `used for varying the speed ratio between shafts 28 and 28 as described herein. Control of this variable ratio is accomplished through shaft-`6|a which has right and left hand threads engaging poppets I4 and |42 which are oscillatably secured to levers |31 and |38 respectively. It is apparent that rotation of shaft Bla in one direction will swing levers I 31 and |38 together at one end and rotation of shaft 61a in. the opposite direction will swing the levers apart at that same end. Rotation of shaft SIa to give the desired control is derived, through safety clutch |43, from shaft 6I aswill be described later.

Regulator shaft 63 is rotatably mounted in the casing of drive unit 21 and has arm 84 secured to its outside end and worm gear |44 secured to its inside end, said worm gear |44 meshing with threads or teeth on shaft Sla so that when shaft 5Ia rotates worm gear |44 'will be moved to oscillate shaft 63. This motion of shaft 53 may be used to control the tightness of the wound roll as described hereinafter.

The shafts 51, 6I and 53 (see Fig. 2) are rotatably mounted by suitable bearings in the casing of control unit 52 and provided with means for preventing end motion. Shaft 8| has secured to it a central member |45 on which bevel gears |45 and |41 are rotatably mounted meshing with bevel gears |48 and |49 which are rotatably mounted on shaft 5|. Bevel gear |48 has secured to it a spur gear |50 ywhich meshes with a similar spur gear |5I secured to shaft 53. Bevel gear |49 has secured to it a sprocket |52 which through chain |53 is chained to sprocket |54 secured to shaft 51. Thus it is apparent that bevel gear |48 will be turned in proportion to the speed of shaft 53 and bevel gear |49 in proportion to the speed of shaft 51. If bevel gears |48 and |49 run in opposite directions at the same speed central member |45 and therefore shaft 8| will remain stationary. Any difference in the speeds of bevel gears |48 and |49 will cause shaft 6I to rotate and control variable speed drive unit 21 as set forth hereinafter. Roll I3 is connected in a like manner by clutch 25 to. output shaft28 of the variable speed transmission drive unit 21 like the unit 23 for the roll I2. The input shaft on unit 21 is indicated at 28. It is possible to disengage the clutches 2| and 25 to allow the reel II and the rolls to revolve to vother work stations, as previously described, bringing the proper roll spindle into alignment, and then engage the clutches with the output shafts 22 and 26, respectively, which drive the respective rolls I2 and I3.

The drive for. units 23 and 21 is from pulley 3|, the latter being driven by the calender rolls on stand I8', by' a chain or belt 32 to thepulley 33 on the main drive, or jack shaft 34. The jack shaft 34 has mounted thereon the sprockets 35,

38, and this jack shaft is also connected to auir-I iliary drive shaft 31 bya clutch 3 8, which clutch allows the drive units 23, 21 to be operated independently of the influence of the main drive through the differential control units to be presently described. Shaft 31 is connected to the in- 3 put shaft 2s of the transmission drive una` 21 for roll I3, by a slip clutch coupling indicated generally at 40 which can be regulated by a lever,

to presently appear, to produce a predetermined degree of torque between drive shaft 31 and the input shaft 28. This coupling consists of a male frusto-conical element4| splined for axial movement on shaft 31, coacting with a female element 42 inthe shape of a cup having a cavity 43 confronting the male element designed to produce the desired torque transfer which in turn controls the web tension. 'I'he female element 42 is fixed to input shaft 28. Chain sprocket 44 fixed to shaft 31, is connected by chain 45 and sprocket 48, provided with a handle 39, to auxiliary drive shaft 41, which latter has a torque transfer coupling 48, 4Ia and 4Ib alike in al1 respects to elements 4I, 42, and 43 of coupling 48. The coupling 48 connects shaft 41 `with input shaft 24 of the transmission drive unit 23which drives roll I2. It will then be obvious that with these couplings 40 andj48 controlling the transfer of torque, the shaft 31 may be driven faster than roll I3 to produce a. tightly wound roll; and on unwinding roll I2, the shaft 41 may be driven slower than the roll I2 `to hold the unwinding web under proper tension.

As the unwinding and winding rolls continue to operate, these rolls vary in diameter at the peripheral surface, and, therefore must vary in rotating speed to maintain a constant web speed. Since shafts 31 and 41 are connected to the calender stack drive, they and their respective' couplings 40 and 48 will operate at fixed speed. The variable drive units 23 and `21 will allow for roll speed changes. As the unwinding roll I2 becomes smaller, the peripheral surface speed tends to increase, and since the web tension must remainV constant, the variable drive units 23 and 21 must beaccordingly adjusted. To accomplish this adjustment a control unit operating on a regulation differential gear principle is introduced into the assembly. An application of the differential gear principle as a control unit is illustrated in the patent to Perry, heretofore indicated. A control unit vof this character for the unwinding roll I2 is indicated at 5I, and the control unit for winding roll I3 is indicated at 52.

The control units 5I and 52 compensate for the difference in speed of the main drive shaft g 34 and the speed of the spindles or shaft speeds of the unwinding and winding rolls I2, I3, respec- .all

tively, and these controls adjust the speed of the drive units. Control unit 52 has its shaft 53 connected by sprocket 54 and chain '55 to the main drive shaft 34 by sprocket 36.. Thus shaft 53 forms the constant speed side of the differential control unit 52', and is connected to the main drive shaft 34 at all times. The opposite side of the differential control unit 52, 'the variable side, is the shaft 51, which is connected by sprocket 58 and chan'59 to sprocket 60 on the input sha't 28 of the drive unit 21. The reactance shaft 8|.

of the differential control unit. that is. the shaft that operates under the influence of difference in speedof constant shaft v.'53 and variable speed shaft 28, is connected directly to the speedadjusting shaft 6I a ofthe transmission driveunit 21. vThis reactanceshaft' 6I in the` differential control unit causes the adjustment. in the drive unit 21 of the ratio of the speedbetweenfinput shaft 28 and the output shaft. 28 whchlatter drives the -winding roll I3. Under operating conditions, reactance shaft 6I attempts to reach a sary to reset the drive units.

neutral position caused by the difference in speed of shafts 53 and 28. In finding the neutral position, the shaft 6| will rotate adjusting shaft SIa and thereby change the adjustment in the drive unit 21 which is designed in such a manner that the resulting angular speed of the paper roll I3 and the main drive shaft 34 will become adjusted to the correct ratio for any diameter of the paper roll.

The web speed being constant, the diameter of the roll I3 increases as it winds up with the resultant progressive decrease in revolutions per minute as it continues to operate. The decrease in speed slows down shaft 28, causing a greater slip in the torque transfer coupling 40, which coupling runs at constant speed. When shaft 28 slows down it immediately produces a. change in the shaft 51 of the differential control unit thereby altering the position of reactance shaft 6| that causes the readjustment of the ratio of the speed, between input shaft 28 and output shaft 26 on the transmission drive unit 21, to the requirement of the moment. This changing of adjustment continues until the roll is wound to full size at which time the machine is shut down and the fully processed roll is moved to the unloading station in the orbit of the reel.

As roll I3 has been decreasing in rotational speed during the winding, the unwinding roll I2 has been increasing in rotational speed because the web speed must remain constant so that it will pass through the calender stack without breaking. In order to produce an increase in the rotational speed of the unwinding roll I2 the control unit 5| has its constant shaft 53a connected to the main drive shaft 34 by chain 55a and sprocket 35. The variable shaft 51a of differential control unit 5| is' connected to input shaft 24 by the chain 59a; while reactance shaft SIb has direct connection with adjusting shaft Gle which changes the speed ratio between input shaft 24 and output shaft 22 ondrive unit 23 for the unwinding roll.. Thus it will be seen that this organization of elements connect control unit 5| with main drive shaft 34, and also connect control unit 5| and drive unit 23, and the speed ratio adjustment of drive unit 23, all of them corresponding to the elements heretofore described in connection withthe operation of winding roll I3,

and it is believed that more details of the description are unnecess^ry in view of their clear disclosure in Fig. 2.

It is evident that at this point where the rolls and cores are replaced variable speed drive units 23 and 21 are set to the position opposite that which is necessary for starting the machines with proper web control. At this position a new unwinding roll would flood the paper into the calenderwhile the winding core could not take up the slack fast enough. It is, therefore, neces- For the purpose of description, a manual resetting will be described,

although a simple motor connection could be used for this purpose. With the machine stopped, clutches 38, 2| and 25 are disengaged. By rotating handle 39 drive units 23 and 21, also shafts 51 and 51a of differential units 5I and 52, will now be rotated, but shafts 53 and 53a of the differential units will not rotate being still chained to shaft 34 which is stationary. With one member of each differential unit stationary and one rotating, the third member of the differential, namely shafts 6| and 6|b, connected to the ratio change screws of the variable speed drive units 23 and 21, will rotate to cause their ratios to change. Handle 39 is rotated manually only long enough to effect total ratio change. When this is done clutches 38, 2| and 25 may be engaged and the drives are set for the next winding and unwinding operation.

Slip clutches 4|) and 48 are set for transferring a predetermined constant value of torque between the auxiliary drive and the rolls. When all conditions are ideal, the amount of torque transferred and the variation of the driving units 23 and 21 should produce a roll which is wrapped uniformlyfor its entire diameter.

It may be found that a uniformly wrapped roll does not prove satisfactory under certain conditions such as under severe changes in temperature or humidity. A roll that is wrapped tightly at the core and more loosely toward the outside would allow for expansion or contraction without any appreciable change in the paper roll diameter. Regulation of the tightness of the wrap can be controlled by a suitable linkage arrangement connected to the speed indicator shaft 63 as shown in Figures 2 and '1. Lever 64 on shaft 63 is connected to male coupling 4| by link indicated generally at 65. As the speed varies, indicator lever 64 will move'carrying with it link 65, thereby changing the adjustment in coupling 40 to automatically control slippage, which in turn determines the tightness of the wrap. The indicator shaft 63 is lgeared (not shown) to shaft 6|a, that is a continuation of reactance shaft 6|, which changes the ratio of speed between the input and output shafts 28 and 26 on the drive unit 21. It is evident that a means is now available to regulate the paper tension both for an unwinding roll and a Winding roll at all roll diameters and that the degree of tightness in the Wrap may be also regulated.

Upon further study of Fig. 1, another important feature of this arrangement is evident. As web I5 is drawn through the calender stack I6, it-is assisting in operating drive unit 23 which throughconnections with the main drive shaft 34 is attempting to retard the roll I2. Drive units 23 and 21 are connected as previously described, thereby causing web I5 to also operate winding roll drive unit 21. In theory, therefore, it would not be necessary to have any drive for the winding and unwinding mechanism. Friction losses in the units, however, require that drive chain 32 from the calender stack I6 be used. It is now standard practice in the trade to hold tension on the unwinding roll I2 by applying a friction brake of some character to the spindle of the unwinding roll, and this practice wastes all the power in the braking friction. With the present invention this. power customarily dissipated is not 10st, but all of it, minus the small loss in gearing and slip in the torque transfer coupling 40 is conserved and is pumped back to help wind the winding roll 3.

In Figures 8 and 9 there is illustrated a modication of elements in the assembly, which elements provide for the substitution of a belt and idler pulley to control the transfer of torque between the drive shaft 31 and input shaft 26 of drive unit 21 for the winding roll I3. Like the automatic slippage to control the tightness of the wrap as depicted in Figure 2 of the drawings a drum pulley 13 is xed on the auxiliary drive shaft 31, and a like pulley 14 is fixed to the input shaft 28 of the drive unit 21 with a flat belt. 15 trained over the pulleys. This arrangement is used .instead of the coupling 40 in Fig. 2 of the drawings. To regulate the tightness of the Wrap invention, the speed indicator arm 64 on 'indicator shaft 63, has a link 8| connecting it to one branch of a rockablebell crank lever 82. The other branch of lever 82 has a link connection 83 with arm 18 (Fig. 9). As the speed indicator arm 64 on drive unit 21 uctuates with the alteration of the speed ratio in this drive unit 21, as heretofore explained, the fluctuations are translated through the linkage 8|, 82, 83, and idler 80 to belt- 15 thereby automatically altering slip between shaft 31 and 28 and'producing variation in the tightness of the wrap on winding roll I3. It will be understood throughout this specification that slip or slippage between shafts alters the amount, or degree, or value of the. torque transferred from one shaft to the other. Y

When the reel |I is moved from one working position to another, it is necessary to provide a quick detachable connection at the clutches 2| and 25 in Figs. 2 and 8 to accomplish this end. In Figs. 10 and 11, an arrangement ofmechanical details for accomplishing this detachability is illustrated. Referring to the clutch 2|, in Figs. l0. and 1l, an operating lever |06 has one end pivoted at |01, to a boss |08 carried by the adjacent transmission drive unit 23 for the winding roll. A pin |09 xed to an intermediate portion of lever |06 slides in a circular peripheral groove |I in the rear end of the sliding clutch collar I I I which is slidably mounted on the output shaft 22 of drive unit 23. The lever |06 in the clutch 25 in Figs. 10 and 11 is constructed exactly like the lever for clutch 2|, and performs the same function, except the lever is connected to the drive unit 21, and the male clutch collar slides on the output shaft 26.

The slidingclutch collar III in Fig. 10 of the drawings, engages with the fixed clutch collar II2 xed to the outer ends of the roll spindles ||3 journalled in the bearings II4, one on the end of each reel arm I Ia. In Fig. 11 of the drawings the fixed clutch collar I I5 is xed to the ends of -the "roll drive shafts I I6. It will be obvious in referring to Figs. and 11 of the drawings, that movement of lever |06 to the left, in Figs. 1.0 and 11, will move the sliding clutch collars I-I I respectively. out of meshing engagement with xed collars II2 on spindle ||3 (Figure 10), and

iixed clutch collars II5 on roll drive shafts I,|6 (Fig. 11). Movement of levers |06 in the opposite direction, or to the right. will bring the sliding clutch collars into meshing engagement, respectively. with the fixed collars on the spindles ||3 and shafts IIB, in which position `they are shown in Figs. 10 and 11.

In Figs. 10 and 11, the elements of promoting ease and despatch of mounting and demounting the rolls are shown. In the form of the invention shown in Fig. 10, the spindles II3 journalled in the bearings II4 in the ends of the arms IIa on one. sideof the reel are formed with tapered chucks II'I which extend into and grip the confronting ends of the tubular core sleeves I|8 on which the rolls of web are wound and unwound, when the cores and rolls are assembled on the reel. The arms Ila on the opposite side of the reel have threaded openings ||8 on the ends of the arms which receive a threaded spindle |20. one for each arm. On the outer ends of these spindles are hand wheels |2I by which'they are turned into and out of engagement with the ends of the core sleeve H8. On the inner ends of each of the spindles |20, is a. tapered head or chuck |22 Which'is journalled for rotation on the spindles so it will rotate with the rolls while the vspindle remains stationary. 'I'he chucks |22, grip l0' the ends of core sleeve |I8 on the inside, when in the engaged relation, as shown in the upper portion of Fig. 10, and when the spindles are backed oil', as shown in the lower portion of Fig. 10, they move'free of the core sleeve. It will then be seen that when the clutch collars I||- |I2 are engaged, and the chucks ||1-|22 are in gripping relation with the core sleeves II8, the rolls I2, I3 will be driven by the respective input andoutput shafts 22-26.

To accommodate the character of spindle |I'6 vided with sectional bearingsjin which the cap portions |23 thereof are pivoted at |24 to the bottom portion |25. Thebottom portions is integral with the ends of the arms IIa as seen in Fig. 12. On the side opposite the pivot |24, the

` cap portions` are formed with an extension |26.

The extension is provided with an enlarged opening |26a which receives a locking bolt|21. These locking bolts have their inner ends pivoted at I2 to the bottom portions A|25 of the bearings so as to permit the bolt to rockwhile the bolt is being trained into and out of the opening I26a to' engaged and disengaged positions to hold the cap portions |23 respectively in closed and released position. On the outer free end of the bolts |21 is threaded a wing nut |29 which locks against the extensions I2'I on the cap portions |23 of the bearings. The nuts are removed from the bolts. and the cap portions |23 are swung to open position on the pivots for the purpose of bodily removing propelling shafts II6 and the rolls carried thereby.

In order to grip the roll core sleeves II 8 and propel the rolls, each of the shafts IIB has a pair of adapters |30, |3I, one adjacent each end, leaving free portions of the shaft to be journalled in the bearings on the ends of the arms. The adapters |30, |3| are secured to the shafts |I6 and they engage the ends of the core sleeve II8. When clutch collar |I5 on the shaft II6 which carries the roll to be demounted, is disengaged from clutch collar III, the reelmay be rotated to a suitable position for removal of the roll. At this position, lock nut |28 is unscrewed, cap |23 is opened and shaft |I6, the roll carried thereby, the clutch collar ,I I5, and adapters |30, I3| are removed as a unit. Adapter I3| is .then removed ratio between the input and output shafts of the transmission drive unit 21. The movement of the male member 4| changes the degree of'torque transferred to the 4female member y42. form of the invention in Figs. 8 and 9, the pressure on pulley bearing on belt 15, is automatically regulated by linkage 64.82, and 83 in re- In the' sponse to the change in the speed ratio between the input and output shafts of the tra'nsmission drive unit 21. The pressure on the belt 15 determines the torque transferred from auxiliary drive shaft 31 to the input shaft 28. This automatic regulation of the torque transferred serves t regulate the tightness of the wrap on the winding roll I3, but is not necessary on the unwinding roll I2.

However, in addition to the mechanism to produce automatic regulation of the torque transmitted from the drive shaft 31, to the input shaft 28, it is sometimes necessary to change or alter the constant value of the torque transferred from shaft 31 to shaft 28; In other words, the automatic regulation may be effective within certain limits, and it sometimes becomes necessary to change the limits. To elect the change in the constant value of the torque transfer from shaft 31 to shaft 28, in the form of the invention in Figs. 8 and 9 of the drawings, the link 83 is parted and the ends are threaded to receive a hand wheel |35 operating on the principle of a turnbuckle, and has a sleeve |36 with right and left hand threads at the opposite ends respectively. The threads on the sleeve engage like threads adjacent the part in the link 83, and when the hand wheel |35 is rotated in one direction greater pressure'is applied to belt 15, and the constant torque value is increased. When wheel |35 is rotated in the opposite direction pressureis released on belt 15 and the constant torque value is diminished. A hand wheel |31 alike in construction and function to wheel |35 is applied to link 65 in the form of the invention shown in Fig. 2 of the drawings. -It follows that the constant value of the torque at the coupling or clut'ch 40 in Fig. 2 of the drawings may be altered in addition to the automatic regulation. Thus the cony stant value of torque transfer between shafts 31 and 28 for the winding rolls |3 is effectivevin both forms of the invention in Fig. 2 and Figs; 8 and 9.

It is also the aim of the present invention to effect the constant value of the torque transferred from shaft 41 to shaft 24 of the unwinding rolls i2 in both forms of the invention. male element 4|a is splined at 4|b, on shaft 41 for movement relative to the fixed female element this movement to any predetermined position will alter the constant value of the torque transferred between the elements in that form of the invention. To change the constant value of the torque transferred by the belt 12 to the shafts 41 and 24, in Fig. 8, arm 11 may be moved from one position to anotheron its pivot 11a. In doing so greater or lesser pressure will be applied to belt 12 with the result that greater or lesser degrees of torque will be imparted to the shafts 41, and 24, and thus the constant value ofthe torque transfer will be effected.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent of the United States is: t

1. In a device of the class described comprising an unwinding roll; a. winding roll; a driving means for the unwinding and winding rolls; a

' main power drive; a drive unit for each roll including coacting shafts, one of which is an input Since responding drive units, another of which is a constantly acting element each of which is connected with the main power drive, and another of which is an element actuated by the differential speed of the other two elements and connected with the third shaft of each of the corresponding drive units; a detachable driving connection between the drive means of each roll and the output shaft of each of the corresponding drive units; a driving connection between each of the input shafts of the drive units and the main power drive; and a device in the last-mentioned driving connection for each of the input shafts to provide a. predetermined torque transfer between the main power drive and the input shafts..

2. In a device of the class described comprising an unwinding roll; a winding roll; a driving means for the unwinding and winding rolls; a main power drive; a drive unit for each roll including coacting shafts, one of which is an input shaft, another of which is an output shaft, and

a third of which adjusts the 'ratio of speed between the other two shafts; a differential control unit for each drive unit including coacting elements, one of which is the variably acting 'element connected with the input shaft of each of the corresponding drive units, another of which is a constantly acting element each of which is connected with the main power drive, and another of which is an element actuated by the differential speed of the other two elements and connected with the third shaft of each of the corresponding drive units; a detachable driving connection between the drive means of each roll and the output shaft of each of the corresponding drive units; a driving connection between each of the input 'shafts of the drive units and the main power drive; a device in the last-mentioned driving connection for each of the input shafts to provide a predetermined torque transfer between the main power drive and the input shafts, and means actuated by the third shaft of the drive unit for the winding roll only and connectedy with the corresponding one of said devices adapted for automatically regulating the tightness of a roll of web wrapped on the winding roll.

3. In a device of the class described comprising an unwinding roll; a winding roll; a driving means for the unwinding and winding rolls; a main power drive; a drive unit for each roll including coacting shafts, one of which is an input shaft, another of which is an output shaft, and a third of which adjusts the ratio of speed between the other two shafts a differential control unit for each drive unit including coacting elements, one of which is a variably acting element connected with the input shaft of each of the corresponding drive units, another of which is a constantly acting element each of which is connected with the main power drive, and another of which is an element actuated by the differential speed of the other two elements and connected with the third shaft of each of the corresponuding drive units; a driving connection between the drive means of each roll and the output shaft of each of the corresponding drive units; a driving connection between each of the input shafts of the drive units and the main power drive a device in the last-mentioned driving connection for each of the output shafts to provide a predetermined torque transfer between the main power drive and the input shafts; and detachable means in the driving connection between the drive means of each roll and the output shaft of each drive unit to permit removal of the rolls without disturbing the position of the output shafts.

4. In a device of the class described comprising an unwinding roll; a winding roll; a driving means for the unwinding andwinding rolls; a main power drive; a drive unit for each roll including coacting shafts, one of which is an input shaft, another of which is an output shaft, and a third of which adjusts the ratio of speed between the other two shafts; a differential control unit for each drive unit including coacting elements, one of which is a variably acting element connected with the input shaft of each of the corresponding drive units, another of which is a constantly acting element each of which is connected with the main power drive, and another of which is an element actuated by the difierential speed of the other two elements and connected with the third shaft of each of the corresponding drive units; a; detachable driving connection between the drive means of each roll and the output shaft of each of the corresponding drive units; a driving connection between each of the input shafts of the drive units and the main power drive; and means connected with the last mentioned driving connection and acnecting each of the last mentioned means and the tuated by the third shaft of 'the drive only for the winding roll adapted for automatically regulating the tightness of a roll of web wrapped on the winding roll.

5. In a device of the class described comprising an unwinding roll; a winding rol1;. a driving means for the unwinding and winding rolls; a main power drive; a, drive unit for each roll including coacting shafts, one of which is an input shaft, another of which is an output shaft, and a third of which adjusts the ratio of speed between the other two shafts; a differential control unit for each drive unit including coacting elements, one of which is a variably acting element connected with the input shaft of each of the corresponding drive units, another of which is a constantly acting element each of which is connected with the main power drive, and another of which is an element actuated bythe differential speed of the other two elements and connected with the third shaft of each of the corresponding drive units; a driving connection between the drive means of each roll and the output shaft of each of the corresponding drive units; a driving connection between each of the input shafts of the drive units and the main power drive; means connected with the last mentioned driving connection and actuated by the third shaft of the drive unit only for the winding roll adapted for automatically regulating the tightness of a roll of web wrapped-on the winding roll; and detachable means in thedriving connection between the drive means of each roll and the output shaft of each drive unit to permit removal of the rolls without disturbing the position of the output shafts.

6. A device of the class described comprising a supporting stand; a reel mounted on the stand to revolve periodically to predetermined working 65 positions and there to remain fixed for a certain period; a pair of rolls journalled on the reel in spaced relation to each other; a work station; a continuous web adapted for winding on one roll as it is unwound from the other roll and hav-y ing a portion intermediate the rolls operated on under constant tension at the work station; a driving means on each roll; a main power drive; means connected with the driving means, one for main driving means; each of said members in-- cluding coasting elements providing slippagebetween the rotational speed varying means and the main power drive; and means including a dierential speed driving means connected to the main power drive and each of the rotational speed varying means arranged to control the rotational speed varying means.

` 7. A device of the class describedcomprising a supporting stand; a reel mounted on the stand to revolve periodically to predetermined working positions and there to remain fixed for a certain period; ya' pair of rolls iournalled on the reel in spaced relation to each other; a work station; a

continuous web adapted for winding on one roll as it is unwound from the other roll and having a portion intermediate the rolls operated on un- Y der constant tension at the work station; a driving means on each roll; a main power drive; means connected with the driving means, one for each roll, for varying the rotational speed of the driving means for the rolls, means including a differential speed driving means connected to the main power drive and each of the rotational speed varying means andV actuated by said dii'- ferential speed driving means whereby to compensate for the variance in the rotational speed in the driving means; a female member having a cavity and connected with each of the rotational speed varying means; and male members on the power drive each having a portion thereof conforming in shape to the cavity and coacting with a female member to provide slippage between the rotationalspeed .varying means and the power drive.

8. A device of the-class described comprising a supporting stand; a reel mounted on the stand to revolve periodically to predetermined working positions and there to remain xed for a certain period; a pair of rolls journalled on the 'reel-in spaced relation to each other, a. work station: a continuous web adapted for winding on one roll as it is unwound from the other roll and having 'including coacting elements providing slippage between the rotational speed varying means and the main power drive in response to the relative speed difference between the rolls and their driv' ing means on the respective sides of the work station; a dierential speed driving means connected to the main powerdrive and each of the rotational lspeed varying means and actuated by the differential speed between the main power drive and each of the rotational speed varying means,

. whereby to compensate for the variance in rotational speed in the driving means; and' means connected with one of the rotational speed varying means and one of vthe coacting elements of vone member adapted for automaticalLv regulating the tightness of the roll of web wrapped on the winding roll.

A 9. A device ofthe class described comprising a supporting stand; a reel mounted on the stand to revolve periodically to predetermined working positions and there to remain xed for a certain each roll, for varying the rotational speed of 76 period; a pair of rolls iournalled on the reel in spaced relation to each other, a work station; a continuous web adapted for winding on one roll as it is unwound from the other roll and having a portion intermediate the rolls operated on under constant tension at the work station; a driving means on each roll; a main power drive; means connected with the driving means, one for each roll, for varying the rotational speed of the driving means for the rolls; a member connecting each of the last mentioned means and the main driving means; each of said members including coacting elements providingslippage between the rotational speed varying means and the main power drive in respon-se to the relative speed difference between the rolls and their driving means on the respective sides of the work station; a differential speed driving means connected to the main power drive and each of the rotational speed varying means and actuated by the differential speed between the main power drive and each of the rotational speed varying means, whereby to compensate for the variance in the driving means; and a detachable means between each of the driving means and each of the rotational speed varying means to permit removal of the rolls for replacement without disturbing the position of the rotational speed varying means.

10. A device of the class described comprising a supporting stand; a reel mounted on the stand to revolve periodically to predetermined working positions and there to remain iixed for a certain period; a pair of rolls journalled on the reel in spaced relation to each other, a work station; a continuous web adapted for winding on one roll as it is unwound from the other roll and having a` portion intermediate the rolls operated on under constant tension at the work station; a driving means on each roll; a main power drive; means connected with the driving means, one for each roll, for varying the rotational speed of the driving means for the rolls; a member connecting each ofl the last mentioned means and the main driving means; each of said members including coacting elements providing slippage between the rotational speed varying means and the main power drive in response to the relative speed difference between the rolls and their driving means on the respective sides of the work station; a differential speed driving means connected to the main power drive and each of the rotational speed varying means and actuated by the diil'erential speed between the main power drive and each of the rotational speed varying means, whereby to compensate for the variance in rotational speed in the driving means; and means on the reel for journalling a third Iroll thereon so as to provide a replacement for the reel unwound.

11. In a device of the class described comprising a pair ofrolls, a continuous web being wound on one roll and unwound from the other and passing therebetween, a driving means on each roll, a main power drive, means connected with the driving means on each roll for varying the rotation speed of the driving means for the rolls, a member connecting each of the last mentioned means and the main power drive, each4 of said members including coacting elements providing slippage between the rotational speed varying means and the main power drive in response to the relative speed difference between the rolls and their driving means, and a diierential speed driving means connected to the main power drive and each of the rotational speed varying means and actuated by the diierential inspeed between the main power drive and the respective first mentioned means whereby to compensate for the variance in the rotational speed in the\driving means.

l2. The combination with a reel for supporting a pair of rolls from one of which a web is wound on the other and between which the web is being worked upon under constant tension of a power drive for the rolls; means connecting the power drive with each of the rolls; each of said means including a unit for varying the rotational speed of the drive for the respective rolls, and also coacting elements effective upon a variation in the relative speed between the rolls and their respective power drives on opposite sides oi' the work to produce a slippage between the power drive and each roll; and a control unit including a differential speed driving means connecting the power drive -with each of the units for controlling the operation of the rotational speed varying units.

CHARLES S. CAFFREY. 

